JP2008528880A - Braking device especially for dual mass flywheel - Google Patents

Abstract

The damping device (1) has a first (2) and second component with friction device (4) inbetween. The second component has two spaced surfaces (5,6) and the first component is mounted between same whilst a third component is likewise mounted between these faces so that the third component (8) and first component during relative movement are braced against one another so that the surfaces of the first and third component are pressed against the surfaces of the second component. The first component can be connected to a drive and the second component to an output or vice versa. An annular space is formed between the two spaced surfaces.

Description

The present invention relates to a braking device, and more particularly, to a dual mass flywheel including a first component, a second component, and a friction device disposed therebetween.

Various types of braking devices have been proposed for vibration dampers, particularly dual mass flywheels. On the other hand, dual mass flywheel spring systems generally operate with very low damping values. In general, a separate damping system helps to achieve a specific attenuation value with precise dynamic parameters. Braking devices with a lubricant having oils acting in the region of the friction surface are known here. On the other hand, the braking device operates in a dry state in order to extract energy from the system by friction under certain load conditions.

The present invention is based on the problem of proposing a new braking system that can be easily integrated into known dual mass flywheels and that provides the necessary damping characteristics in an optimal manner.

The problem is that the second component has two remotely spaced surfaces, the first component is disposed between the surfaces, and from the third component disposed between the surfaces. Also configured, where the surface of the first and third components presses against the surface of the second component when the third component and the first component move toward each other It is solved by a general braking device supported in such a way.

The inventive braking device is therefore supported by relative movement towards each other and the components are pressed against each other to provide various components that create friction. Since the braking device has few components, this allows it to be integrated into the dual mass flywheel in various areas.

One variant provides provision that the first component can be coupled with the drive and the second component can be coupled with the output. As an alternative to this, however, the first component can be coupled with the output and coupled with the drive of the second component.

It is particularly advantageous if a ring-shaped space is formed between remotely spaced surfaces. This is preferably achieved by the ring-shaped formation of the components delimiting the space. At least a portion of the third component is then disposed in the ring-shaped space, and the friction surface is preferably disposed in the ring-shaped space.

A ring-shaped space can only be indicated by the first and second components. It is however also essentially closed radially outwards. It also forms a chamber in which, for example, several individual items of the components described so far can be worn out on the surface of this space which exists radially outside.

However, the ring-shaped space forms a great advantage that it is suitable for receiving lubricant. It can therefore keep the oil or liquid lubricant placed in the friction device, which can provide optimum wetting of the friction surface against which the lubricant is applied.

It is particularly advantageous if the lubricant can penetrate the ring-shaped space radially from the inside, if this lubricant can also leave this space. In doing this, it is proposed that the ring-shaped space has openings for the inflow and outflow of lubricant. In one exemplary embodiment, the surface of the ring-shaped space that radiates inward is completely open to the components projecting in the space, while the ring-shaped space that radiates outwardly. The surface of the space has holes through which the lubricant can reach radially outward.

An advantageous variant embodiment provides for the first and third components to be movable relative to each other between the surfaces of the second component and to be arranged to move with respect to the second component. do. The surface of the second component thus forms a boundary between which the first and third components are placed. These surfaces of the second component are, for example, parallel and flat surfaces that form a rectangular space between them to receive the first and third components. However, the rectangular cross-section of this space must not be larger than the entire peripheral area, rather the cross-sectional area acts to act through the space delimiting the frictional surface in the braking device Can change.

The third component has two assemblies arranged on each one side of the first component to act on the first component when the component is supported relative to each other from two sides. It is proposed. This reduces the transverse force generated by supporting the component, or at least is limited to a smaller value. Furthermore, the structure allows various wedge surfaces and tilt angles to be placed on different sides of the first component, thereby allowing multiple possibilities of affecting the friction value.

All interacting surfaces of the first, second and third components can comprise a friction surface. It is advantageous if the opposing component formed as a ramp is formed without a friction surface and the third component present on the opposite side of the second component has at least one friction surface.

The friction surface can have a texture, for example, it can be grooved or grooved. Here, the structure can extend radially to the friction surface or can be rounded into a circular shape. The friction surface can now be provided on the third component or on the second component. Depending on the application, it may be convenient to have friction surfaces on both sides.

In one exemplary embodiment, the third component facing the first component has at least one slope and the first component facing the third component has at least one slope. Prepare. These slopes lead to supporting the components in relation to each other and increase the friction between the third component and the second component.

These slopes can be shaped as desired to introduce different friction values as required. In particular, the dynamic behavior of the friction device is taken into account. The inclination can thus be formed as an oblique plane or other curved surface to achieve a continuously defined increase in friction during pulling, at the latest after the clearance angle.

The ramp may be formed integrally with the metal sheet that is fixed to or encloses the metal sheet. Here, the wedge is preferably formed of plastic or metal. They can be cast, poured or sintered. Simple manufacture of the slope is achieved by stamping or drawing the slope on a metal sheet.

It is convenient if a clearance angle is provided here. This is achieved, for example, such that the third component is movable by a clearance associated with the first component. This clearance allows rotation with minimal frictional stress in a specific range of rotation of the first to second components relative to each other, with adjacent slopes providing a coefficient of friction for further rotation due to the slope of the slope. increase.

A convenient brake arrangement provides provision for the first component to have a flange that effectively connects with the spring system. Here, the first flange preferably extends radially from the friction surface of the inner braking device and is connected there with a flange that leads radially outwards to hit the spring.

The second component also preferably has a flange connected to the spring system. The flange can also be configured as a double flange with a flange that effectively connects with the first component extending therebetween.

Such an arrangement also makes it possible to arrange a flyer that is also effectively connected to the spring system, in addition to a flange that is effectively connected to the spring. However, the braking device need not have a flyer. It can be configured, for example, as a damped friction disc where the first and second sides connect directly with the spring.

The first and second components serve to move the force from the first side onto the second side via the spring system, while the flyer keeps the spring of the spring system radially inward Because they are useful, they are not drawn too far radially outward by the acting centrifugal force.

An alternative embodiment prepares the first component to have a plate-shaped part with a flange that is in effective connection with the spring. This plate-shaped part serves to increase the main mass and is constituted by the required mass, so that each reaches the required main mass. It is convenient if this plate-shaped part has a starter ring gear.

In order to guarantee a simple structure of the braking device, it is proposed that the flange and the plate-shaped component which are effectively connected to the spring are detachably connected to each other. This detachable connection is preferably achieved by engagement such as, for example, spline engagement.

It is proposed that the sealing agent be arranged between the spring and the flange and plate-type components that are effectively connected, especially if the braking device comprises a lubricant. This sealing agent can extend in a disc shape around the center of the braking device and prevent the penetration of lubricant from the side of the spring on the opposite side of the sealing agent.

It is particularly proposed for this that the sealing agent has a sealing plate and at least one sealing lip. The sealing lip can for example cooperate with an axially extending flange.

The described structure of the braking device allows the friction device to be arranged radially at the top of the spring system or outside the spring system. This also allows the use of a lubricant present in the region of the spring for the friction device. Placement within the spring system is also possible if sufficient axial structural space is obtained.

A possible axial arrangement adjacent to the spring is also possible, so that the friction device is axially on the side of the spring system that is on the opposite side of the component that can be connected to the drive. Proposed to be deployed.

In the figure, two exemplary embodiments of the braking device are described and described in further detail below. It should be noted here that the main and second aspects can be interchanged without departing from the spirit of the invention. The main side can be arranged outside, including all, and the second side is further arranged inside, or the main side is arranged inside, while the second side is It means forming an outer ring.

The braking device 1 shown in FIG. 1 is connected to a first component 2 that can be connected to the crankshaft of the motor as the main side, and to a connection and gear as the second side. It consists essentially of a second component 3 that is possible. A friction device 4 is provided between the first component 2 and the second component 3.

The second component 3 has two remotely spaced surfaces 5 and 6, and the flange 7 of the first component 2 is in the space between these remotely spaced surfaces 5 and 6. Project. In the space between the remotely spaced surfaces 5 and 6 of the second component 3, the third component 8 lies with the beveled surfaces 9 and 10 on the opposite side of the first component. It is disposed on its side surface with a friction surface 11 on its side surface that is on the opposite side of the second component.

The oblique surfaces 9 and 10 are arranged between two slopes 12 and 13 which are fixed to the flange 7 of the first component 2, so that with the relative movement between the components 2 and 3, the oblique surfaces 9 and 10 The surface 9 cooperates with the slope 12 or the oblique surface 10 cooperates with the slope 13. The slanted surfaces 9 and 10 are a bit from the corresponding slopes 12 and 13 so that after the movement within the clearance angle, the slanted surfaces 9 and 10 only exist so that they touch the slopes 12 and 13. Placed apart. In the case of rotation beyond the clearance angle range, the oblique surface cooperates with the inclination so that the friction facing 11 of the third component 8 rubs against the side surface 5 of the second part 3, where the inclination 12 , 13 and the angle of the oblique surfaces 9, 10, the friction on the friction surface 11 increases or decreases in accordance with the degree of rotation of the first and third components relative to each other.

By supporting the first and third components in relation to each other, however, not only the third component 8 pressed via the friction surface 11 onto the side surface 5 of the second component 3 but also the first The radially outer end of the flange 7 of the first component 2 is also pressed against the side surface 6 of the second component 3. In order to increase the friction in this region, the friction surface 14 is also provided at the radially outer end of the flange 7 where the friction surface 14 cooperates with the side surface 6 of the second component 3.

The cooperation of the first, second and third components is illustrated once again in FIG. FIG. 2 a shows the basic position in which the flange 7 and the third component 8 of the first component 2 exist such that they can move freely between the two sides 5 and 6 of the second component 3. Indicates. Both the friction surface 14 provided on the flange 7 of the first component 2 and also the friction surface 11 provided on the third component 8 are only slightly away from the surfaces 5 and 6 of the second component 3. And the beveled surfaces 9 and 10 on the third component 8 are remote from the slopes 12 and 13 of the flange 7 of the first component 2.

In the exemplary embodiment of FIG. 1, the main wedge 15 having the slopes 12 and 13 is fixed to the radially outer end 16 of the flange 7 of the main part 2. In the third component 8, the third wedge 17 is fixed to a ring-shaped disk 18.

However, the wedges 15 and 17 can also act directly on the end 16 of the flange 7 or the ring-shaped disc 18 of the third part 8, for example by deformation.

A comparison of FIGS. 2 a and 2 b shows that the third wedge 17 is the main wedge without reducing the gap 19 between the friction surface 14 on the flange 7 of the first part 2 and the side face 6 of the second part 3. 15 indicates that it can move within the clearance angle range. In addition, the clearance 20 between the friction surface 11 and the side surface 5 of the second part 3 is not reduced by movement within the clearance angle range. This occurs, for example, when idling or operating with a constant load. Here, only the spring system is stressed and there is little friction on the friction device. This clearance angle generally exists between ± 3 and ± 7 °, for example approximately ± 6 ° in a diesel motor.

2b and 2c compare the friction surface 11 with respect to the further relative movement of the flange 7 of the first part 2 relative to the third component 8 after the third wedge 17 abuts the main wedge 15. And 14 indicate that they are pressed against the side surfaces 5 and 6 of the second part 3. The wedges 15 and 17 slide over each other and the gaps 19 and 20 are zero. The wedge 15 on the main side pulls the third wedge 17 and, due to the generated axial force, provides itself with a torque that prevents the relative rotation of the wedges. This results in a damping or friction device 4.

The first component 2 connected to the second component 3 on the second side via the flange 7 and the friction device 4 is a further flange that cooperates with the spring 22 as a spring abutment on the main side. 21. Two flanges 22 and 23 extending radially outward and inward act as spring abutments on the second side. The flange 22 is connected to a ring-shaped component 24 that forms the contact 6 via a flange 23, and the flange 23 is fixed to the component 24 by a pin 25. The pin 25 further forms an abutment 5 and connects a further ring-shaped component 26 with the flanges 22 and 23 which can be connected to a connection or gear.

Ends 29 extending radially inside the flanges 22 and 23, on both sides of the flange 21, as a ring-shaped component, holding the spring 22 and radially preventing the centrifugal force acting on the spring, A flyer 27 or 28 with 30 is arranged in each case.

The flange 21 of the first component 2 has an axial extension 31 that cooperates via a splined engagement with a side plate 32. The horizontal platen 32 is connected by a screw 33 having a plate-shaped sheet metal or cast part 34. This plate-shaped part 34 is therefore considered as the main mass and is formed with different materials and different sizes according to the required mass requirements. Further in this embodiment, a starter ring gear 35 is provided at the radially outer end of the plate-shaped part 34.

A disc-shaped sealing plate extending substantially radially from the flange 31 extending axially to the outermost end of the braking device 1 between the plate-shaped part 34 and the flange 22 which are also present on the main side 36 is arranged. At the radially inner end of the sealing plate 36, the sealing lip 39 is arranged with an L-shaped reinforcement 37 and a clamping ring 38 facing the flange 31 extending in the axial direction. An L-shaped seal can also be envisaged which can be injected directly onto the sealing plate 36-for example as a PTFE seal lip.

The sealing plate 36 can be connected to or connected to the housing at its radially outer end (not shown). A region acted upon by the lubricant is thereby created on the left side of the sealing plate 36 in the drawing, where the springs and friction devices are arranged. This space is sealed by the sealing plate 36 so that the lubricant cannot reach the plate-shaped part 34.

The braking device 40 shown in FIG. 3 has a first component 41 on the main side, i.e. a second on the second side which can be connected to the crankshaft, connection or gear of the motor. And the friction device 43 disposed therebetween can be connected.

In contrast to the illustrated embodiment of FIG. 1, the friction device 43 is configured with double flow. For this reason, the friction device is made up of parts that are configured in the first component 41 in mirror images that cooperate from two opposing sides. To this end, the second component 42 has two spaced apart surfaces 44 and 45 between which one end 46 of the first component 41 is disposed.

In addition, between these surfaces 44 and 45, two third components 47 and 48 are configured in the mirror image and a third wedge 49 or 50 is fixed and arranged, respectively. The third wedges 49, 50 cooperate with the main wedges 51 and 52 fixed to the end 46 of the main component 41, so that the third component main component 41 and parts 47 and 48 of With respect to the relative movement between the first component 41 and the third component 47, 48, the lateral surfaces of the components 47 and 48 are relative to the surfaces 44 and 45 of the second component 42. It is supported to be pressed.

This process is illustrated once again in more detail in FIG. FIG. 5a shows how the end 46 of the main component 41 together with the main wedges 51 and 52 is in the second configuration until the main ramps 51 and 52 exist opposite the third ramps 49 and 50. It indicates whether it is free to move within the range of motion above a particular clearance angle in connection with element 42. With further movement of the wedges relative to each other, the wedges 49 and 50 are pressed against the abutment surfaces 44 and 45. In doing so, the friction surfaces 53 and 54 disposed on the parts 47 and 48 position themselves relative to the sides 44 and 45 so that the friction is the first on the major side. Occurs between component 41 and second component 42 on the second side.

Two surfaces 44 and 45 that serve as abutments for the friction surfaces 53 and 54 are provided in the ring-shaped components 55 and 56. These ring-shaped components 55 and 56 are then placed in a ring-shaped support component 57 that extends essentially in the axial direction. Together with the ring-shaped component 56, the support component 57 forms a contact surface on the second side for the spring 58 and is a cup-like component 59 connected to a flange-like component 46. Has a radial extension 60 which serves as an abutment surface on the main side for the spring 58.

The cup-like component 59 has a shorter radial extension 61 between the radial extensions 60, on both sides of this radial extension 61, at their radially outer ends. The flyer plates 62 and 63 or 64 and 65 that are riveted together are arranged to be freely movable. The flyer plates that are connected to each other can also be screwed, welded, or connected by traction fixation. These flyer plates hold the spring 58 with radial extensions and prevent centrifugal forces acting on the spring 58.

The surrounding ring 66 holds the plate 57 and is fixed to the support plate 57 as well, and serves just as an additional mass like the surrounding ring 67 that serves as a fixing ring for connection to the link. Works.

A cup-like component 59 is connected radially inwardly with a ring-shaped component 68 which has an engagement and thereby is connected to a plate-shaped component 69. The plate-shaped component 69 has a hole 70 through which the entire first component 41 can be secured to a crankshaft (not shown). Furthermore, the plate-shaped component 70 is configured as an additional mass, has a trigger engagement 71 for measuring the rotational speed, and a shoulder for receiving a toothed ring (not shown). Having a radially extending portion.

Between the plate-shaped component 69 and the spring 58 and the friction device 43, a sealing plate 72 having a sealing lip 73 on its radially inner side is arranged. The seal lip 73 seals the axially extending component 68 on the major side and a ring-type seal that cooperates with a housing wall (not shown) on its radially outer end. 74. The sealing plate 72 thus delimits the area of the spring 58 and friction device 43 acted upon by the lubricant and prevents the lubricant from exiting towards the plate-shaped component 69.

In the drawing
Shows a partial cross-sectional view of a braking device having a friction device with a wedge system located on the main side, Shows the cooperation of the friction surfaces of the friction device shown in FIG. Shows a partial cross-sectional view of a braking device having a friction device with a wedge system located on both sides from the main side; Shows a top view on the friction device cut from FIG. 3, and Shows the cooperation of the friction surfaces of the friction device shown in FIG.

Claims (27)

A braking device, in particular for a dual mass flywheel, comprising a first component and a second component and a friction device arranged between them, wherein the second component comprises two Having a remotely spaced surface, wherein the first component is disposed between the surfaces, and a third component is similarly disposed between the surfaces, wherein the third configuration When the element and the first component move towards each other, the surfaces of the first and third components are supported in such a way that they are pressed against the surface of the second component. Braking device characterized in that. 2. A braking device according to claim 1, characterized in that the first component can be connected to a drive and the second component can be connected to an output. The braking device according to claim 1, characterized in that the first component can be connected to an output and the second component can be connected to a drive device. Braking device according to any of the preceding claims, characterized in that a ring-shaped space is formed between the remotely spaced surfaces. 5. Braking device according to claim 4, characterized in that the ring-shaped space is radially closed outwards. 6. Braking device according to claim 4 or 5, characterized in that the ring-shaped space has a lubricant. The braking device according to claim 4, 5 or 6, wherein the ring-shaped space has an opening for inflow and outflow of lubricant. Braking device according to any of the preceding claims, wherein the first and third components are movable relative to each other and to the second component A braking device characterized in that it is arranged between the surfaces of the second component as possible. Braking device according to any of the preceding claims, wherein the third component is characterized in that it has two assemblies each arranged on one side of the first component. apparatus. Braking device according to any of the preceding claims, characterized in that the third component present on the opposite side of the second component has at least one friction surface. apparatus. 11. A braking device according to claim 10, characterized in that the friction surface is grooved or grooved. Braking device according to any of the preceding claims, characterized in that the third component facing the first component has at least one slope. Braking device according to any of the preceding claims, characterized in that the first component facing the third component has at least one slope. 14. Braking device according to claim 12 or 13, characterized in that at least one slope has a curved surface. 15. A braking device according to any of claims 12 to 14, wherein the tilt is characterized in that it is pushed or pulled by an enclosing sheet. Braking device according to any of the preceding claims, characterized in that the third component is movable by a clearance associated with the first component. A braking device according to any of the preceding claims, wherein the first component has a flange operatively connected to a spring system. Braking device according to any of the preceding claims, characterized in that the second component has a flange operatively connected with a spring system. 19. Braking device according to claim 17 or 18, characterized in that, in addition to a flange operatively connected to the spring system, a flyer operatively connected to the spring system is also arranged. Braking device. Braking device according to any of the preceding claims, characterized in that the first component comprises a flange and a plate-shaped part which is operatively connected to the spring. 21. Braking device according to claim 20, characterized in that the plate-shaped part has a starter ring gear. 22. Braking device according to claim 20 or 21, characterized in that the flange and the plate-shaped part operatively connected to the spring are detachably engaged with each other, preferably connected through engagement. 23. Braking device according to claims 20-22, characterized in that a sealing element is arranged between the spring and an effectively connected flange and plate-shaped part. 24. Braking device according to claim 23, characterized in that the sealing element comprises a sealing plate and at least one sealing lip. 25. Braking device according to claim 24, characterized in that the sealing lip cooperates with an axially extending flange. Braking device according to any of the preceding claims, characterized in that the friction device is arranged radially at the apex of the spring system or arranged outside the spring system. Braking device according to any of the preceding claims, wherein the friction device is pivoted on the side of the spring system that is on the opposite side of the component that can be connected to the drive device. A braking device characterized in being arranged in a direction.

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